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Design and Analysis of Cyclone Seperator
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Design and Analysis of Cyclone Seperator
Bharath Raj Reddy Dere1
1Mechanical department
Chaitanya Bharathi Institute Of Technology
Hyderabad,India.
A . Divya Sree3,
3Mechanical department
Chaitanya Bharathi Institute Of Technology
Hyderabad,India.
G. Mahesh Babu
2,
2Mechanical department
Chaitanya Bharathi Institute Of Technology
Hyderabad,India
S. Rajiv Rao4
4Mechanical department
Chaitanya Bharathi Institute Of Technology
Hyderabad,India.
ABSTRACT: The gas-solids cyclone separator is industrial
equipment that has been widely used. Due to its industrial
relevance, a large number of computational studies have been
reported in the literature aimed at understanding and
predicting the performance of cyclones in terms of pressure
and velocity variation. One of the approaches is to simulate
the gas-particle flow field in a cyclone by computational fluid
dynamics (CFD).
The cyclone performance parameters are governed
by many operational parameters (e.g., the gas flow rate and
temperature) and geometrical parameters. This study focuses
only on the effect of the geometrical parameters on the flow
field pattern and performance of the tangential inlet cyclone
separators using, CFD approach. The objective of this study is
three-fold. First, to study the optimized stairmand’s design by
understanding the pressure and velocity variations. Second, to
study the performance of a cyclone separator by varying its
geometrical parameters. Third, to study the performance of a
cyclone separator by varying its flow temperatures. Finally to
study the performance of a cyclone separator with collector
and compare to that without collector. Four geometrical
factors have significant effects on the cyclone performance
viz., the inlet width, the inlet height and the cyclone total
height. There are strong interactions between the effect of
inlet dimensions and the vortex finder diameter on the cyclone
performance. In this study, inlet geometry, cone- tip diameter,
cone height is taken for analysis.
The modeling of the cyclonic flow by
computational fluid dynamics (CFD) simulation has been
reported. The effect of the cone tip-diameter, cone height and
inlet geometry in the flow field and performance of cyclone
separators was investigated because of the discrepancies and
uncertainties in the literature about its influence. The flow
field pattern has been simulated and analyzed with the aid of
velocity components and static pressure contour plots. The
CFD model was used to predict the pressure and velocity
variations of cyclone geometries based on Stairmand’s high
efficiency design.
1. MODELLING
1.1 THE STAIRMAND OPTIMIZED DESIGN
Stairmand’s conducted so many experiments on
the cyclone separator and finally developed the optimized
geometrical ratios. By considering this geometric ratio’s
the modeling of the cyclone done in solid works.
.
Figure 1.1.1: cyclone geometry in solid works
TABLE 1: Cyclone geometry used in this simulation (stairmand’s
optimized design) Geometry a/D b /D D
x/D
S /D h /D H
/D
B /D
Stairmand’s
High Efficiency
0.5 0.2 0.5 0.5 1.5 4 0.375
1.2. MODELLING IN SOLID WORKS
To design the cyclone the diameter (D) is
considered as 20 mm.
Step 1: Draw the sketch according to the stairmand’s ratios.
Step 2: specify the dimensions.
Step 3: Revolve the sketch 360 degrees and give thickness
as 0.1mm.
Step 4: to get the inlet, draw a rectangle on the part which
is developed by revolving.
Step 5: extrude the rectangle along the Z-axis (L=D).
Step 6: draw a rectangle on the extruded plan to get the
hallow inlet. Select the rectangle and give extrude cut
throughout the extruded rectangle.
Step 7: save the geometry.
International Journal of Engineering Research & Technology (IJERT)
Vol. 3 Issue 8, August - 2014
IJERT
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ISSN: 2278-0181
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Fig 1.2.1 shows the dimensions of the cyclone separator
Fig.1.2.2 cyclone separator design.
Fig.1.2.3 Half sectional view of cyclone.
2.
GOVERNING EQUATIONS
2.1 CONTINUITY EQUATION
The continuity equation describes the conservation of
mass.
Consider a differential control volume
Let ‘ρ’ be the density of fluid, ‘u’ be the x-component, ‘m’
be the mass of fluid element
dxdydz)]
x(/=[m
a=
(density) b=u (velocity)
a’= dxx)/( b’=u+ dxxu )/(
fig.4.1.1 fluid particle differential control volume
0]=
)V(
.+t /
[
0=w)z(/ +v)y(/ +u)x(/+t /
0=dzdy dx
w)z(/+dzdy dx
v)y(/
+
dzdy dx
u)x(/+
dz)dy dx t(/
0=efflux
Mass
+onaccumulati
of
Rate
Since,
dzdy dx
w)z(/=direction-in xefflux
Mass
dzdy dx
v)y(/=direction-in xefflux
Mass
dxdydz
u)x(/ =direction-in xefflux
Mass
dz)dy dx
t(/=
volumealdifferenti
mass
of
change
of
Rate
International Journal of Engineering Research & Technology (IJERT)
Vol. 3 Issue 8, August - 2014
IJERT
IJERT
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13
]W+Q=E[
dxdy yx)]u+yyy(v/ +xy)v+xxx(u/
+vfy+[ufx = )W( done work of rate Total
forces) surfaceby done(work
+ forces)body by done(work =done work Total
y x velocitForce=done work of Rate
dxdy ]yT/?+xT/K[ =Q
n)(conductiogradient etemperatur
due surface acrossfer heat trans gConsiderin
?dxdy v^2)]+(u^2 1/2+[eD/Dt =
element fluid ofenergy totalchange of Rate
v^2)]+(u^2 1/2+[eD/Dt =massunit
per element fluid ofenergy totalchange of Rate
v^2)+(u^2 1/2+e=
massunit per fluid ofenergy Total = E
]W+Q=E[
dW/dt+dQ/dt =dE/dt
forces surface
andbody todueelement fluidon done work of rate
+element fluid intoheat offlux Net
=element fluid theinsideenergy of change of Rate
element. fluid moving a toamics thermodynof law -I g
applyinby derived becan equation energy The
EQUATION ENERGY 2.2
2222
]yT/+xT/K[ = y]T/ v+x
Tu
t
T[ C
]yT/+xT/K[ =DT/Dt C
y)v/+x u/ ( =yx=xy
yv/ =yy
xu/ =xx have We
yxy u/+xy x v/ +yy y v/
+xx x u/ + ]yT/+xT/K[ ==De/Dt
yx)]dxdyu+yyy(v/ +xy)v+xxx(u/
+vfy+[ufx +dxdy ]yT/+xT/K[
=v^2)]dxdy +(u^2D/Dt 1/2+[De/Dt
2222
P
2222
P
2222
2222
2.3 Significance of k-ɛ equation
K-epsilon (k-ε) turbulence model is the most
common model used in Computational Fluid
Dynamics (CFD) to simulate turbulent conditions. It is a
two equation model which gives a general description
of turbulence by means of two transport equations (PDEs).
The original impetus for the K-epsilon model was to
improve the mixing-length model, as well as to find an
alternative to algebraically prescribing turbulent length
scales in moderate to high complexity flows. The first
transported variable determines the energy in
the turbulence and is called turbulent kinetic energy (k).
The second transported variable is the turbulent dissipation
( ) which determines the rate of dissipation of the
turbulent kinetic energy.
3 .CFD ANALYSIS
3.1 STAIRMAND’S OPTIMIZED DESIGN
ANALYSIS: Open Ansys work bench and Select fluent
analysis system for the current analysis.
Fig.3.1.1. fluent project schematic
3.1.1 CYCLONE GEOMETRY
Import the cyclone design from the solid works.
open the design modeler. Click on generate the imported
geometry appears. Select the part body in the tree outline
.select the body click on the screen. Change the solid body
into the fluid body. Close the design modeler and save the
project.
Fig.3.1.2: solid cyclone geometry for the simulation.
3.1.2 MESH
Open mesh.>create named sections
1. Select the inlet face.name it as velocity inlet
2. Select the outlet face and name it as pressure outlet.
3. Select the rest of the faces and name them as wall.
Select mesh in tree outline. In mesh details default
conditions are set to be CFD and FLUENT solver as shown
in the fig 5.1.3. Give high smoothing condition and fine
relevance. And change the transition slow to fast to reduce
the no. of elements. Select mesh and click generate mesh to
obtain mesh. The generated mesh contains 74128
International Journal of Engineering Research & Technology (IJERT)
Vol. 3 Issue 8, August - 2014
IJERT
IJERT
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tetrahedron elements and 14577 nodes. Close the mesh and
update the mesh in project schematic.
Fig.3.1.3: mesh details and no of elements
Fig3.1.4: mesh top view
Fig 3.1.5: mesh front view
3.1.3 SETUP
Double click on the fluent set up to set the
simulation conditions. The software automatically
recognizes the 3d dimension. The display mesh after
reading, embed graphics windows and work bench color
scheme must be enabled. Enable the double precision and
serial processing options. Then click ok to open the fluent.
Fig. 3.1.6: fluent launcher
STEP 1: General > check mesh (To verify the mesh is
correct or not)
Enable pressure based type, absolute
velocity formulation and transient time steps.
Fig.3.1.7: general conditions
STEP 2: In models select the realizable k-epsilon (2eqn)
model and enable the enhanced wall treatment because the
design contains many walls.
Fig.3.1.8: defining the models
STEP 3: Boundary condition 3.1. Velocity inlet> z-velocity =20 m/s
Turbulence: specification method> k-ɛ model
Fig.3.1.9: inlet velocity boundary conditions.
3.2. Outlet Turbulence: specification method> k-ɛ
model
Backflow Turbulence kinetic energy= 5 m2/s2
Backflow Turbulence dissipation rate=10 m2/s3
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Fig.3.1.10: outlet boundary conditions.
3.3. Wall
Wall motion> stationary wall
Shear condition> no slip
STEP 4: Solution methods
Fig.3.1.11: details of solution methods
STEP 5: Initialization: Select standard initialization and
compute from inlet velocity
Fig.3.1.12: initialization conditions
STEP 6: RUN> Check case>close
Time step size(s) =1; Number of time steps =50; Max.
Iterations / time step = 20 > calculate
Fig.3.1.13: set up for the calculation
3.1.4 SOLUTION
Residuals
Fig.3.1.14 residual graph
The solution is converged at the 355th
iteration.
The vector fig 5.15 shows that the path followed by the
fluid inside the cyclone. The flow follows swirl flow
conditions as explained in the principle of the cyclone
separator. The left side bar shows various velocity ranges.
The color obtained in the vectors show the variation of
velocity at the different sections. The values of the velocity
can be studied from the left side scale. To understand the
complete flow inside the cyclone the contours at the z=0 is
computed. The velocity and pressure contours are shown in
fig 5.1.16. which gives complete flow variation in the
cyclone separator.
Vectors
Fig.3.1.15: vectors of velocity
Pressure- velocity contours
The pressure in the cyclone separator increases
from the center to wall. The maximum and minimum static
pressures are 4.122e+002 (pa) and -6.44e+001 (pa)
respectively. The velocity first increases then decreases
from center to towards wall. The maximum and minimum
velocity magnitudes are 23.62 m/s and 0 m/s respectively.
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Fig.3.1.16: the pressure and velocity contours at the section
Z=0 .
Pressure-velocity charts
The following charts shows the pressure and
velocity variation along the y-axis at different sections. The
graphs are plotted with y-axis as pressure/velocity and x-
axis as radial distance along the x-axis.
Table 2: The sections
SERIES 1 AT Y=0
SERIES 2 AT Y=0.01
SERIES 3 AT Y=0.02
SERIES 4 AT Y= -0.01
SERIES 5 AT Y= -0.02
Graphs: The graphs are drawn by taking y-axis as
pressure/velocity and the x-axis as radial distance along X.
fig.3.1.17: the pressure and velocity graphs at different section along the
y-axis.
3.1.5 RESULTS AND DISCUSSIONS
The stairmand’s optimized design results are
shown in above graphs. To study the variations in pressure
and velocity 5 different sections are created along the y-
axis as shown in the table 5.1.1. The variation in the
pressure and velocity inside the cyclone is shown in the fig
5.1.16 & fig 5.1.17. The solution got converged at the 15th
time step, total time is 15s.
The pressure inside the cyclone along the radial
distance (x-axis) increases from centre to the ends. The
pressure variations are also shown as a graph in fig5.1.17.
The shape of the graph is U which shows the fall down of
pressure at the centre of the cyclone (x=0).
The velocity in the cyclone along the radial
direction first increases and then decreases from centre to
the wall. The shape of the graph is inverted W which
shows the fall down of velocity at the centre and at the
wall. The high velocity obtains in the middle portion of the
centre and the wall.
3.2 TEMPERATURE ANALYSIS
This analysis involves various flow studies at
various temperatures. The stairmand’s design is used for
the simulation in fluent. The same set up is used for the
temperature analysis as the stairmand’s design analysis.
Additional to that energy equation is activated to start the
temperature analysis. In the velocity inlet boundary
conditions the temperature of the inlet flow is added. This
study involves in the simulation of the cyclone at 4
different temperatures. The variations in the pressure and
velocity are noted and compared. The effect of the
temperature is justified.
The analysis is done at the temperatures
290,300,310 & 320 (k).
3.2.1 SOLUTION Table 3: pressure and velocity readings at different temperatures
Temp (k) 290 300 310 320
Maxpressure (pa) 533.5 535.35 522.15 522.6
Mini pressure(pa) -185 -192.7 -194.7 194.7
Maxvelocity (m/s) 25.25 25.22 25.12 25.12
Minivelocity (m/s) 0 0 0 0
Graphs: The graphs are drawn by taking y-axis as
pressure/velocity and the x-axis as radial distance along X.
Graph 3.2.1 The variation of pressure velocity in cyclone and at section
Z=0 .
`Pressure contours
Fig 3.2.1 variation of pressure along the radial distance (x-axis) at z=0.
velocity contours
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Fig 3.2.2 variation of velocity along the radial distance (x-axis) at z=0.
3.2.2 RESULTS AND DISCUSSIONS
The results are concluded that the cone height has
significant effect on the performance of the cyclone. The
pressure in the cyclone varies along the X-axis as shown in
the contours. The pressure first decreases and then
increases. The minimum pressure occurs at the mid section
(x=0). The graph shows the variation in the pressure along
the radial direction. The curve is in U shape explains the
decrease and increase of pressure. The velocity in the
cyclone first increase from the centre and then decreases at
the wall. The curve will be in M shape or reversed W
shape. The velocity is high at the middle portion of the
center and the wall.
The variation in the flow temperature slightly
varies the pressure for every 20k. The velocity of the flow
doesn’t vary with the temperature. So we can say that the
temperature cannot affect the performance of the cyclone
because of the slight variations we can neglect the effect of
temperature.
3.3 THE ANALYSIS OF STAIRMAND’S DESIGN
WITH COLLECTOR
The collector is the attachment to the cyclone
where the particles are collected. Collector is of any shape
(ex: cube, cylindrical). It locates at the end of the cone tip
and it prevents the re-entertainment of particles. In this
analysis a cube shaped collector is provided at the bottom
(with dimensions 15mm*15mm*15mm). The same set up
is used to simulate the cyclone with collector.
3.3.1CYCLONE GEOMETRY and MESH WITH
COLLECTOR
Fig 3.3.1 geometry of cyclone with collector
Fig 3.3.2 mesh of the cyclone with collector
‘
3.3.2 SET UP IS SAME AS THE STARMAND’S
DESIGN ANALYSIS
3.3.3 SOLUTION
The solution of the simulation of the cyclone with
collector is compared with the cyclone without collector.
The variations in pressure and velocity are noted and
compared & the cyclone performance is justified.
Table 4: The pressure and velocity readings.
Without collector With
collector
Max pressure (pa) 418.5 403.4
Mini pressure (pa) -66.28 -55.11
Maxvelocity (m/s) 23.65 23.5
Minivelocit (m/s) 0 0
Graphs: The graphs are drawn by taking the y-axis as
pressure/velocity and x-axis as radial distance along X
Graph 3.3.1: variation of pressure and velocity.
Pressure contours
Fig 3.3.3 variation of pressure along the radial distance (x-axis) at z=0.
International Journal of Engineering Research & Technology (IJERT)
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velocity contours
Fig 3.3.4 variation of velocity along the radial distance (x-axis) at z=0.
3.3.5 RESULTS AND DISCUSSIONS
The results are concluded that the cone height has
significant effect on the performance of the cyclone. The
pressure in the cyclone varies along the X-axis as shown in
the contours. The pressure first decreases and then
increases. The minimum pressure occurs at the mid section
(x=0). The graph shows the variation in the pressure along
the radial direction. The curve is in U shape explains the
decrease and increase of pressure. The velocity in the
cyclone first increase from the centre and then decreases at
the wall. The curve will be in M shape or reversed W
shape. The velocity is high at the middle portion of the
center and the wall.The study shows that the collector
doesn’t have much effect on the cyclone performance.
There are slight variations in the pressure and velocity
which can be neglected.
3.4 INLET GEOMETRY The inlet geometry is one of most important
parameter which affects the cyclone performance. This
study involves with various inlet geometries. By varying
the height and width of inlet the inlet geometry varies. The
analysis of 3 different cyclones with different inlet
geometry is simulated in the fluent. By comparing all the 3
cyclones th ne better design is concluded. The same set up
is used for the simulation as stairmand’s design analysis.
3.4.1 SOLUTION
Table 5: pressure and velocity readings
a=12,
b=6
a=10 ,
b=5
a=8, b=4
Max pressure (pa) 513.5 415.7 334.8
Mini pressure (pa) -102.9 -76.28 -46.68
Maxvelocity (m/s) 24.25 23.84 22.89
Minivelocity (m/s) 0 0 0
Graphs: The graphs are drawn by taking the y-axis as
pressure/velocity and x-axis as radial distance along X
Graphs 3.4.1 the pressure and velocity plots
Pressure contours
Fig 3.4.1 variation of pressure along the radial distance (x-axis) at z=0.
Velocity contours
Fig 3.4.2 variation of velocity along the radial distance (x-axis) at z=0.
3.4.2 RESULTS AND DISCUSSIONS
The results are concluded that the cone height has
significant effect on the performance of the cyclone. The
pressure in the cyclone varies along the X-axis as shown in
the contours. The pressure first decreases and then
increases. The minimum pressure occurs at the mid section
(x=0). The graph shows the variation in the pressure along
the radial direction. The curve is in U shape explains the
decrease and increase of pressure. The velocity in the
cyclone first increase from the centre and then decreases at
the wall. The curve will be in M shape or reversed W
shape. The velocity is high at the middle portion of the
center and the wall.
The inlet geometry is the most important
geometrical parameter of the cyclone design. By varying
the inlet dimensions there is a huge variation in the
pressure and velocity. The maximum pressure in the
cyclone falls drastically by the decrease in the inlet
International Journal of Engineering Research & Technology (IJERT)
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dimensions. For every 2mm decrease in the inlet height and
1mm decrease in width gives 20% decrease in the pressure.
By the decrease of this inlet dimensions the pressure drop
also decreases and we can say that the one with minimum
pressure drop is works more efficiently. So the inlet
dimension shows a large effect on the performance of the
cyclone. The velocity also decreases by the increase in the
inlet geometry, if velocity decreases the collection
efficiency decreases so the inlet dimensions must be high.
So the cyclone with the inlet height 10mm and inlet width
5mm is better design.
3.
CONCLUSIONS
After studying the existing literature and
performing analysis on certain cyclone parameters, the
following conclusion can be drawn:
The separation mechanism inside cyclone
separators is not well understood yet, and needs
more investigations.
Nearly all published articles have no systematic
and complete study for the effect of geometrical
parameters on the flow field and performance.
In all operating conditions and cyclone types the
FLUENT CFD was found to be much closer to the
experimental measurement.
This project is done taking into consideration
single parameter at a time, the results may vary if
multiple parameters are considered at a time.
Some parameters have less interest compared with
others like the effect of inlet conditions and
cyclone height.
Ex: 1. A cone is not an essential part for
cyclone operation, whereas it serves the
practical purpose of delivering collect
particles
to the central discharge point.
Ex: 2.Comparison between cyclone with
and without dustbin was done and
observed that a negligible effect of the
dustbin on the performance
REFERENCES
[1] Khairy Elsayed 2011, PhD thesis on Analysis and
Optimization of Cyclone Separators Geometry using RANS
and LES Methodologies. Pages from 20-160. [2] John Anderson 2011, A Text Book on Computational Fluid
Dynamics, vol. 1
International Journal of Engineering Research & Technology (IJERT)
Vol. 3 Issue 8, August - 2014
IJERT
IJERT
ISSN: 2278-0181
www.ijert.orgIJERTV3IS080015
(This work is licensed under a Creative Commons Attribution 4.0 International License.)
20